Shaping machine



4 r H. w. ZIMMERMAN ,220, 2

SHAPING MACHINE Filed Oct. 4, 19s? 11 Sheets-Sheet 1 Nov. 5, 1940.

SHAPING MACHINE Filed 001;. 4, 1937 11 Sheets-Sheet 2 1940. H. w. ZIMMERMAN ,2 0,38

SHAPING MACHINE Filed Oct. 4, 1937 11 Sheets-Sheet 3 Nov- 5, 940- H. w. ZIMMERMAN ,3

SHAPING MACHINE Filed Oct. 4, 1937 11 Sheets-Sheet 4 Nov. 5, 1940. H. w. ZIMMERMAN srmme MACHINE Filed Oct. 4, 1937 11 ao n-squt 7 Nov.5,.1940. H. w. .ZIMMEIRMAN v2,220,382 t SHAfING MACHINE Filed Oct. 4, 1931 11 Shuts-Sheet 8 Nov. 5, 1940.

w. ZIMMERMAN SHAPING MACHINE Filed Oct. 4, 1937 11 Shoqts-Sheet 9 l bruml b ln l.

H. w. ZIMMERMAN 2,220,382

SHAPING MACHINE Filed Oct. 4, 1937 11 shins-sheet 1o Nov. 5, 1940. H. w. ZIMMERMAN 2,220,382

SHAPING MACHINE Filed Oct. 4, 1957 11 Shoots-Sheet 11 Patented Nov. 5, 1940 i t I UNITED STATES PATENT OFFICE SHAPING MAGHIN'E Herman W..Zimmerman,- Highland Park, 111., as-

signor to Automotive Maintenance Machinery 00., North Chicago, Ill., a corporation of Illinois Application October 4, 1937, Serial No. 167,157 I I 24 Claims. (CL 90-38) My invention relates to a shaping machine and foregoing character thatembodies a tool supportit has to do particularly with a power machine of mg and operating ram and which includes imthe foregoing character which is well adapted for proved mechanism for operating the ram and for shaping both large and small pieces of metallic adjusting both the length of and the position of work having various shaped surfaces. the ram stroke. H :5

The shaping machines heretofore available Another object is to provide a machine of the have been large and cumbersome devices thatare foregoing character having a work support table of a highly complicated and expensive nature. adapted for both vertical and lateral movements The working space required for the same and the and which embodies improved'means for accomcost thereof prohibit the use of such machines plishing such movements. To this end, my in- 0 in the smaller work'or service shops. Such mavention contemplates mechanismfor feeding the chines greatly increase the cost of work to be table laterally of the direction of movement of done because of their larger size and because of the shaping tool, which mechanism is connected the time required to handle them and set them to the main drive by means which maintains a up for any particular piece of work. There is constant operating relation between the drive and, a demand for a metal working machine in bethe feeding mechanism notwithstanding adjusttween the drill press and the lathe which will ment of the work support at an angle to the handle the shaping of a flat or irregular surmovement of lateral feed. face and, from the standpoint of the small shop An additional object is to provide an improved owner, the model worker, and the experimental drive connection between the power drive mech- 2O worker, a great need exists for a shaping machine anism and the mechanism for feeding the work which serves the foregoing purpose, which resupport laterally, which includes a flexible drive quires but little working space, and is of an inmember adapted to accommodate turns, bends, expensive nature. Because of the foregoing conandthe like, therein, to facilitate drive connecditions, it has been necessaryfor the small worktion with the work Support, in various vertical 25 shop operator to resort to the use of makeshift positions of the latter, without change in the tools and devices with the result that his findrive relation between the conni'ected parts. ished work has been unsatisfactory and compara- Still another object is to provide a novel contively expensive in many cases. duit or sheath for a flexible drive member adapted One of the objects of this invention is to proto be reciprocated therein for transmitting mo- 30 vide a machine of the foregoing character which tion from one part to another; which sheath is fully meets the foregoing need. so constructed and arrangedthat, while it may Another object is to provide an improved shapbe flexed throughout its length to various shapes, ing machine adapted for shaping both large and it will not expand or'contract ,to any material small pieces of work of various regular and irregextent whereby the flexible" drive member is held ular shapes, which machine is of a comparatively. against flexing and buckling in all flexed posisimple and inexpensive nature, is of comparativetions of the sheath, and the drive relation between 1y light weight and can readily be moved about the drive and driven parts remains constant noty the Operator, is so compa t that it occupies withstanding the flexed position or condition of but a comparatively small space, and is capable t Sheath A of perfor i a highly efficient manner with Another object of the invention'is to provide reduced spemting and mamtenance costsan operating mechanism for actuatingthe tool A further obJect is to provide an improved she carrying ram which includesa drive crank memt machme of the foregomg Phamter.whlc.h her and improved structure for supporting the is adapted to perform the shaping operations in a precision manner with a minimum of adjustment and attention on the part of the operator, the arrangement of parts being such that adjustments may be made easily, quickly and accu- Stroke h shapmg tool V lately and the machine as a Whole m be Other obgects and advantages W111 become apnism and for adjustably connecting it to such drive mechanism for variation in the-length of latter in close relation to the mainqdrivemecha 5 nipulated so easily and quickly that the shaping. parent as this description progresses and by operations are greatly speeded up and themareference to the drawings wherein chine lends itself well to manual training work in Figu e 1 is a side elevational view of one form schools as well as the other places above menof shaping machine embodying my invention; tioned. I Fig. 2 isa front elevational view of the struc- A further object is to provide a machine of the ture shown in Fig. 1; 5

Fig. 3 is a top plan view of the structure shown in the previous figures;

Fig. 4 is an enlarged partial longitudinal sectional view taken substantially along line 44 of Fig.

Fig. 5 is a fragmental transverse sectional view taken substantially ,on line 5-5 of Fig. 4;

Fig. 6 isa fragmental View of the crank and rocker structure shown in Fig. 4, the same being viewed fro the side of the machine 0 o ite m pp g at a position convenient for the operator.

that shown in Fig. 4;

Fig. '7 is an enlarged fragmental section taken substantially on line of Figs. 6 and 9 and illustrating part of the connection between the ram operating crank and the drive mechanism; Fig. 8 is an enlarged fragmental sectional view taken substantially on line 8-8 of Fig. 6 and further illustrating a part of the structure shown in Fig. 7;

Fig. 9 is a horizontal sectional view further illustrating the driving mechanism and the connections between such mechanism and the work supporting feed mechanism, which view is taken substantially on line 99 of Fig. 5;

Fig. 10 is an enlarged sectional view taken substantially on line llll0 of Fig. 9;

Fig. 11 is an enlarged sectional view taken substantially on line H-H of Fig. 9 and illustrating a part of the mechanism by which drive motion is transmitted to the: work support feeding mechanism;

Fig. 12 is an enlarged and somewhat distorted horizontal sectional view through the mechanism for feeding the work support table in lateral direction, which view is taken substantially along line l2l2 of Fig. 13;

Fig. 13 is a verticalsectional view taken approximately along line i3l3 of Fig. 9 and also of the end portion of the drive conduit between the power drive mechanism and the mechanism for feeding the work support laterally of the machine;

Fig. 17 is an assembly view, partially in section, of the end fitting member supporting the.

end of the conduit shown in Fig. 16;

Fig. 18 is a vertical sectional View of a modified form of mechanism for transmitting feed motion from the driving mechanism to the work support feeding mechanism;

Fig. 19 is a section taken substantially along line l9-I9 of Fig. 18;

Fig. 20 is a view similar to Fig. 18 of still another form of mechanism for imparting drive motion to the mechanism for feeding the work support in lateral direction;

Figs. 21 and 22 are views similar to Figs. 18 and 20 of still further modified forms of mecha- -nisms for imparting motion to the table feeding mechanism;

Fig. 23 is a fragmental sectional view of a hygdraulic device by which motion may be transmitted from the driving mechanism to the table feeding mechanism; and

Fig. 24 is a fragmental top plan view of another part of the motion transmitting mechanism adapted to be associatedwith the structure of Fig. 23 and which, together with the structure of Fig. 23, is adapted to apply an oscillating intermittent motion to the table feeding mechanism from a continuously rotating driving mechanism.

General structure In general, the structure illustrated in the drawings includes a stand 30 of sufficient height to support the operating parts of the machine The stand is provided with legs 3| (Fig. 1) having feet 32 (Fig. 3) which provide a frame support and which, if desired, may be secured to a floor or other suitable supporting surface. If desired, the feet 32 may be provided with casters (not shown) for ready portability of the structure. The stand is further provided with a horizontal shelf 33 beneath its top 34 and this shelf supports a motor 35 which drives the mechanism to be described hereinafter.

The shaping machine mechanism includes a base 36 which has. an upstanding housing portion 31 (Figs. 1, 2, 3 and 5) which encloses a portion of the driving mechanism which imparts reciprocatory movement to a tool carrying ram 38. The forward end of the ram 38 supports a tool head 39 in which is secured a shaping tool 49 (Figs. 1 and 4). At the forward end of the housing 31, I provide a work supporting table 4| which is adapted for both vertical and lateral movements for properly positioning the work with respect to the tool 40 and for feed of the work laterally for making cuts of various widths and at various positions along the work. The work supporting table 4| carries a suitable vise structure 42 (Figs. 1 and 4) in which the Work 43 is secured in proper operating relation with respect to the shaping tool 40. The same driving mechanism that drives the ram 38 forward and backward is also utilized to impart lateral feed movement to the work supporting table 41 and this is accomplished by means of a flexible .drive connector 44 and ratchet mechanism 45 (Figs. 1 and 9-to 12, inclusive) which will be described indetail hereinafter.

Main drive mechanism The drive mechanism includes, in addition to the motor 35, a drive belt 5!! (Figs. 2 and 3) connected with a relatively small pulley 5| on the motor drive shaft 52 and a larger pulley 53 on a cross shaft 54 carried by a bearing member 55 suitably carriedby the top 34 of the table 30.

The shaft 54, at its end opposite the pulley 53, is provided with a step pulley 56 (Figs. 2 and 3) which is drive-connected to another step pulley 5'! carried by a cross shaft 58 journaled in the housing 37. The cross shaft 58, within the housing 31, supports a comparatively small gear 59 (Fig. 4) which meshes with a large gear 60 having a tubular hub portion 6| (Figs. 4, 5 and 9) which extends through the side wall of the housing 3'! and'finds rotative bearing in a laterally extending bearing boss 62 projecting from the side of the housing 31. The gear hub 6| extends through and beyond the boss 62 and a collar 63 ismounted on its outer end for securing the same and the gear 60 rotatably in the boss 82. In'this way the inner end of the boss 82 serves as athrust bearing for the gear 60, and the drive action applied through the gear is more efiicient due to the closeness of the power application to the rotatable support for the gear.

-The gear 60 is, preferably, made of a suitable fibrous material and, for that reason, its hub 6| is formed separately therefrom (Figs. 5, 8 and 9'). More particularly, the face of the gear 60 opposite the boss 62 is provided with an annular recess 60 in which a large annular flange 6| at the end of the hub 6| is received and secured by screws, or other fastening devices, 64. For a reason which will become obvious, the hub flange 6l is thicker than the depth of the gear recess 69*. The hub 6|, just inwardly of its flange 6P, is provided with a somewhat reduced annular portion which is also received in an axial opening in the gear 66, the main bearing portion of the hub being of still further reduced diameter to properly engage in the gearing boss 62. It will be seen from the foregoing that, when the motor 35 is cut in, the gear 60 is continuously driven rotatably at a predetermined speed which may be determined by the particular conditions of use.

The ram and its drive connections The rain 38 is of a sufliciently strong construction to readily withstand the usages to which a machine of this character is subjected, and it is slidably mounted in the top of the housing 31 by a dove-tailed slide connection 38 (Figs. 2 and 5).

The ram 38 is driven backwardly and forwardly through the gear 66, and the mechanism for accomplishing this is of such character that the greatest driving efficiency from the power applied is utilized by locating the power transmitting connections as closely as possible to the gear 66 and its supporting shaft 6 I.

Specifically, referring to-Figs. 6, 7, 8 and 9, the ram drive connections include a crank member 65 which is adjustably connected directly to the gear 66 in such a way that, by adjusting the same along the diameter of the gear, the crank arm may be lengthened or shortened to lengthen or shorten the stroke of the ram. The crank 65 takes the form of an elongated flat plate-like arm having near one end thereof a cylindrical crank arm 66 (Fig. 9). The central portion of the gear hub flange 6W is provided with an annular recess 6| (Figs. '7 and 9) in which is received an annular disk-like plate 61 to which is secured a stud 68 that passes axially through and beyond the end of the gear hub 6!. The outer surface of the disk 61 is flush with the outer surface of the hub flange 6N, and the hub flange 6| and the plate 61 are provided with aligned diametrical dove-tail slots forming a continuous slot 69 passing through both thereof. The crank 65 is provided with side edges suitable for dove-tailed connection and it is slidably received in the slot 69 where it is clamped in any predetermined longitudinally adjusted position by applying axial pressure to the screw stud 68 to place inward tension on the plate 61. More particularly, theouter end of the screw stud 68 receives a nut 68 which seats against certain eccentric drive mechanism (Figs. 9 and 10) which will be described later. By tightening the nut 68, the disk plate 61 and stud 68 are pulled axially inward relative to the hub flange 6| thereby clamping the crank against the dove-tail groove surfaces in the hub flange 6 l on the opposite sides of the hub flange recess 6|". By loosening the nut 68 the crank may be slidalong the dove-tail groove 69 to position its crank arm 66 closer to or farther away from the axis of rotation of the gear 60, thereby shortening or lengthening the crank arm for varying the stroke of the ram 38.

The crank 65 is connected to the ram 38 through a rocker I (Figs. 4, 5, 6 and 9) which is disposed in a generally vertical position in the housing 31. The lower end of the rocker is rockably supported at H upon a cross shaft 12 carried by the housing 31. The upper end of the rocker 10 passes upwardly through an elongated opening 3'! (Fig. in the top wall of the housing 31 and into the ram which is of inverted U-shape in cross section. The upper end of the rocker is connected to the ram 38 by a link 13 pivotally connected at one end, as at 14, to the rocker and at its other end, as at 15, to a depending lug 16 carried by the ram 38. The upper Wall of the ram is provided with an elongated slot 11 through which passes a threaded lug stud 18 adapted to be secured adjustably at different positions along the slot 11 by a nut 19. It will be seen that, with the construction just described, rock movement of the rocker l0 backwardly and forwardly will impart like movement to the ram 38 and, by positioning the rocker attachment lug 16 at different positions along the ram slot Ti,

the position of beginning and ending of the stroke of the ram may be varied to suit the particular shaping conditions to be carried out.

. Rock movement of the rocker 10 is accomplished through the crank 65 as follows: The rocker I0 is provided with a longitudinally extending slot 80 (Figs. 4, 6 and 9) having squared side surfaces providing a slideway in which a slide block 8I-is slidably received. The slide block BI is provided with an annular opening in which the crank arm 66 is rotatably received, and the crank arm and block are held in this operative condition by a washer 82 secured in place by a threaded stud 83 passing therethrough into a threaded opening in the crank arm 66. With the foregoing parts connected in this manner, rotation of the gear 60, in turn revolving the eccentrically located crank arm 66, causes the block 8| to reciprocate in the rocker slideway 6D and move the rocker lflfrom one side to the other of the axis of the gear imparting a power rock movement thereto and to the ram 38 (Figs. 4, 5, 6 and 9).

Tool carrying head ram in which is received a metallic plug 95 having a Wedge surface complemental to and engaging the wedge surface 92 of the shank. The

outer end of the ram opening 94 is threaded for I reception of a threaded screw 96 which forces the plug 95 inwardly against the wedge surface 92 thereby locking the tool head 39 against displacement from the ram and also locking the tool head in any desired position to which it may be rotated for properly positioning the shaping tool 40 with respect to the work.

The tool head 39 is further provided with a squared face 91 which seats against a complemental squared surface at the front end of the ram for holding these parts in true axial alignment and against displacement in the operation of the tool. The front end of the tool head supports a tool carrier 98 which supports the tool 40 in such a way that it may be adjusted vertically relative to the head. The tool holder 98 is carried by a vertically shiftableunit 99 which is connected 'to the tool head through ,a dovetailed slot arrangement I00, and which is adjustable vertically by a screw I I, passing through the unit 99 and the portion of the head which is directly connected to'the ramv 38. Thisadjustment, together with the'shank connection 9|, provides a tool mounting of universal character,

Woflc table and its mounting The work table 4| is carried by a vertically shiftable carriage member ||0 (Figs. 4-and 9) which is slidably connected with theforward end of the housing 31 for vertical adjustment movement. To this end, the forward end-of the housing 31 is provided with a slide track III and the carriage IIO is provided with a slide seat portion 0 which is slide connected to the track III by a dovetailed slide slot II2. One side of the dovetail connection just referred'to takes the form of a clamp block III confined between the forwardtrack wall of the housing 31 and an inclined surface III on the'carriage H0. or more clamp screws I I I' which when tightened move the clamp block to lock the carriage in its vertical position.

Vertical slide adjustment'of the carriage is accomplished by a screw member |I3 (Figs. 1, 2 and 4) threadedly engaging a base portion H4 in the machine base 36 and projecting upwardly from the latter to engage the lower side portion of a lug H5 at the bottom'of th'e carriage IIO. By rotating the screw H3 in clockwise direction,- the carriage IIO may be raised-and by rotating such screw in the reverse direction the carriage may be lowered. a

The work table 4| is connected tothe carriage II!) for transverse slide movement and,

a to that end, the table is provided with a rear wall IIB (Figs. 4 and 11) adapted to be slidably interlocked with and supported by vertically spaced transverse flanges II! and- H8 forming a transverse track on the forward portion of the carriage I I0. The interlock between the table and the flange II! is of the dovetail type while that between the flange H8 is of such character as to permit ready detachment and separation of the parts. Specifically, the top wall of the table is provided with a rearwardly extending flange II9 which overlies and rides upon the upper edge of the carriage flange II8, and the table flange H9 has a transverse locking plate I20 detachably secured thereto which projects into a suitable recess inwardly of the upper edge of the flange M8 to prevent outward displace- 'ment of the table while permitting of lateral slide movement thereof.

The forward end of the work table 4| is separately supported for Work alignment purposes and also for facilitating and insuring free lateral sliding movement of the table without wedge or cramping action. To this end, the forward end of the machine base is provided with an upstanding standard I2I (Figs. 1, 2 and 4) upon which is slidably received a horizontal transverse plate member I22 adapted to engage the lower edges of the side walls 4|? of the work table. The plate I22 is adapted to be locked in position at the desired position along the standard |2I by a locking screw I23 and the plate is of sufficient length to support one or both of the side walls of the work table throughout the entire lateral feed movement of such table. In vertically positioning the table with the structure above described, the adjusting screw II3 maybe first The clamp block is wedged in place by one actuated torset the table at the proper position. When th s. is-=:done,'the front supporting plate I22 isthenmoved to firmly engage the forward In the'use of a tool of this character, the ram 38- is moved forwardly during'the cutting stroke. The tool 40 is so mounted in its holder l0 that, on the back stroke of the ram, it is free to move upwardly away and release itself from the work to permit the back travel of the ram without any cutting operation. Also, it is customary in many shaping operations to feed the work supporting table transversely of the cutting tool and I providefeed mechanism for that purpose. In the structure illustrated, the arrangement is such that the work table 4| is fed laterally of the cutting tool during the backward, non-cutting stroke of the ram, and-this transverse movement may be caused to take place in either direction relative to the cutting tool. In other words, the table remains stationary during the tool cutting operation but, as the tool conditions itself for a new cut, the table moves laterally to position the work for such new cut.

The mechanism for feeding the table transversely includes a. transverse screw I40 (Figs. 2, 4,9, 11 and 12) extending laterally between the carriage flanges III and H8 and having its outer endrotatably mounted in the adjacent end of carriage H0 and secured therein against longitudinal displacement by lock collars MI and I42 (Fig. 12) secured thereon. A suitable nut memberI43 is secured to the back wall IIB of the work table and it is engaged by the screw I40 in such a way that, by rotating the screw in one direction, the table 4| will be shifted toward the right; as viewed from the front of the machine and, by rotating it in the opposite direction, the table .will be shifted oppositely. The outer end of the screw I 40 is provided with a handle I44 through whichit may be actuated to manually shift the table, if that should be desired. In the general operation of the machine, however, the table is shifted automatically in proper timed relation "with respect to the movements of the ram 38' and I will now describe the mechanism by which such movement may be accomplished. The outerend portion of the screw I40 is providedwith an axially shiftable gear I50 (Figs. 1, 2, 9 an d 12) :which is normally connected thereto'for driving motion therewith by apin I5| (Fig.'l2) engaging in a slot I52 in the hub portion of the gear. The slot extends to one end of the gear I50, permitting the hub portion |50 of the gear to-be grasped and slid axially along the shaft towardthehandle I44 for purposely disengaging the gear I50'from operative relation with the screw I40 to permit hand operation of the screw I40 without actuating'the automatic feed mechanism v with which such gear I50 is connected. Theinoperative position of the gear just referred to is illustrated by-the dotted line position of the gear unit shown in Fig. 12.

The gear I50 is normally connected to the main drive mechanism contained within the housing 31 by mechanism which includes a larger gear I53 rotatably mounted upon the outer end of a shaft I5 1 journaled in a bracket F55 mounted on the rear portion of the carriage Ht. It will be seen that connection between thegears E50 and I53 is broken when the former is moved to its dotted line position of Fig. 12. Gear I53 is retained in position on the outer end of the shaft 154 by the hub portion of a pawl unit l5! which is fixedly secured to the shaft I54 by a pin I56 The pawl unit is operatively connected with the teeth of gear I53 and by rocln'ng the shaft IN back and forth the gear I53 is intermittently rotated, in turn, imparting similar movement to the feed screw I 10.

The pawl unit I 5? (Fig. 12) includes a casing I 58 having a cylindrical chamber I59 disposed in alignment with the teeth of the gear I53. A pawl member I66 extends through the chamber I59 and easing P58 into engagement with the teeth of the gear I53. The pawl I66 is yieldably retained in operative engagement with the gear teeth by a spring I62 mounted in the chamber I59 and confined between a screw plug I63 and an enlarged guide hearing it on the pawl member. The spring IE2 permits the pawl Itt to slip over the teeth of gear 553 in the backward motion of the pawl unit and it also permits manual outward movement of the pawl to disengage the same from the gear I53. This latter action may readily be accomplished by a finger piece IE5 onthe outer end of the pawl stem I50.

The gear-engaging end of the pawl I63 is provided with a tip having a right-angled shoulder HiI on one side and a tapered surface IBI on its other side whereby, when it is engaged with the teeth of the gear I53 and moved forwardly, it will act to positively impart motion to the gear but, when it is moved in the opposite direction, the inclined surface ItI will cam the pawl element E56 inwardly against the action of spring 552, permitting the pawl to be retracted to a starting position without transmitting movement to the gear. For example, assuming that the pawl element is engaged with the gear in the manner shown in Fig, 13, counterclockwise movement of the pawl will rotate the gear I53 in like direc tion and cause feed of the screw I46 in one direction but, when the pawl is moved in the opposite direction, the table will remain stationary.

The pawl member is so constructed that it may be reversed in order to reverse the direction of feeding movement of the table. To that end, the pawl member E60 is so constructed as to permit of rotation thereof to reverse the gear pickup action of the pawl tip. Specifically, the pawl casing 558 is provided at its outer open end with diametrically opposed notches I66 and the finger piece 55, to which the pawl member 0655 is fixed by a pin 365*, is provided with a diametrically depending tongue l6? adapted to fit into the notches I66. The right-angled and inclined surfaces of the tip of the pawl member I68 are so related to the notches IE6 that, when the finger piece tongue Mil is engaged therein as shown in Fig. 13, the pawl is set for movement of the gear 53 in one direction. However, when the finger ,piece E85 is pulled outwardly and rotated to reverse the positions of the pawl tip surfaces, as shown in Fig. 1-5, the pawl structure is set for movement of the gear I53 (and the work table) jin the opposite direction. Also, by moving the finger piece $65 outwardly and turning it out of engagement with the notches I66, the tongue I6I will ride on the outer surface of the pawl casing I58 and hold the pawl element out or engagement with the teeth of gear I53, permitting the Work table to be manually adjusted laterally by operation of the handle I44.

From the foregoing, it will be seen that, by rocking the shaft I54 back and forth, the pawl unit will be moved back and forth, thereby imparting feed movement to the screw I46 and the work table 46. The shaft I5 1 is rocked back and forth by means of a flexible drive connection between such shaft and eccentric mechanism actuated by the main gear 66 and its hub BI as hereinabove mentioned.

- Worlc table feed drive connection The drive connection for the work table feed mechanism includes an arm Ill] (Figs. 9, l1 and l2 fixed at one end to the shaft Hi l and pivotally connected at its other end to the upper end of a link ill. The lower end of the link I? Iis connected to a slide block or piston member I12 reciprocably guided in a vertically disposed chamber H3 in a bracket member I'M carried by the carriage Ill}. The piston I12 is connected to the main drive mechanism by a flexible drive wire H5 which is sheathed in a guide conduit H6 which will be described in more detail hereinafter. One end of wire I is secured to the slide block H2 and its other end is secured in another piston-like slide block Ell mounted in a vertical slide chamber in a bracket IlB carried by the bearing boss 62 on the housing 37. One end of the guide conduit H6 is connected by a suitable fitting I19 to the bottom of the bracket I'M and its other end is connected by a similar fitting N9 to the bottom of the bracket H8 so that the wire throughout its movement for reciprocating the slide block In in accordance with reciprocatory movements given to the slide block I". The slide block I'I'I is pivotally connected at I to depending ear I8I of an eccentric strap I82 (Fig. 10). The eccentric strap IE2 is mounted upon an eccentric member I83 which is operatively clamped and secured to the outer end of the gear hub 6i as best shown in Fig. 9. Specifically, the stud 68 which passes through the Il5 is guided id with the hub and also to lock the crank 65 in its predetermined adjusted position as hereinabove mentioned. In order to operably confine the eccentric strap I82, the outer peripheral edge of the eccentric i83 is provided with a circumferential enlarged flange (Fig. 9) which, together with the locking collar 63, serves the intended purpose. In order to hold the eccentric in properly centered relation with respect tothe gear 60 and its hub 6|, I employ a pin I66 passing through aligned openings in the eccentric and the outer end of the hub 6|. With this construction, as the gear 60 is rotated, in turn for moving the work table 4| laterally of the Work.

The flexible drive connection between the main drive mechanism and the lateral feed shaft I40 permits of vertical adjustment of the work table 4I without the necessity of changing or adjusting the drive connection between these parts. This is an important feature of my invention to the end of facilitating the carrying out of the shaping operations and speeding up of such work. In machines heretofore employed, the drive connection between the parts in question has been of such character as to require some compensating adjustments in the drive connections in the case of vertical adjustment of the work tab-1e. The flexible drive connection, including the wire I15 and its sheath I16, is so constructed and arranged that it may be flexed and bent as desired to accommodate the adjustment in question and the sheath is so constructed that the drive wire I15, although flexible, is prevented from buckling or becoming distorted in any way, upon pressure being applied longitudinally thereto, thereby avoiding any change in the effective driving length of the connection which might, in turn, if it should take place, change the relative feed stroke at different positions of the table.

Drive sheath or conduit To the foregoing end, I employ a novel form of sheath which, in its assembled relation to the. driving structure, may be readily flexed and bent but which is not subjected to any material expansion or contraction which might tend to permit the wire I15 to buckle. The sheath, while flexible, performs its function in all flexed conditions similarly to a rigid close-fitting conduit around the wire I15. Specifically, referring to Figs. 16 and 1'7, the sheath I16 takes the form of an outer covering I90 formed of fabric or other similar material. Next to this covering there is a layer of rubber I9I which is vulcanized to a sectional, flexible type of metal tubing I92 comprised of a plurality of interlocking flexible sections which permit of a contracting action but prevent expansion. This metal tubing is of such character that it will permit the same to be flexed angularly in bent formation without separating the sections that form the tubing. Within the metal tubing I92, I provide a spring wire I93 having the coils thereof formed in close fltting relation so that the spring is capable of being expanded but not compressed. By associating the contractible (but not expansible) tubing I92 with the non-contractible (but expansible) spring wire I93 and by locking them together as a unit in their extreme non-expansible and noncontractible conditions, I provide a tubing which is neither contractible nor expansible to any material extent but which is capable of being bent or flexed Without distorting the guide passage in the conduit for the wire I15. The inside diameter of the wire I93 is such that the wire I15 fits snugly therein and the entire arrangement is such that any tendency of the wire to buckle when endwise pressure is applied thereto is entirely avoided in all flexed conditions of the cable.

The sheath sections are fixedly connected together at the ends of the sheath by fittings already indicated, respectively, by the numerals I19 and I19 Since these fittings are identical, only one will be described in detail. The fitting I19 includes a threaded nozzle portion 200 (Figs.

16 and 17) and has'an opening 20I extended axially therethrough for slide guidance of the Wire I15. The nozzles 200 are adapted to be screwed, respectively, into the bottoms of the piston block chambers I14 and I18. Each nozzle has a depending, tubular, externally threaded portion 202, the outer end of which is provided with an annular series of flexible fingers 203 which, together with the tubular portion 202, are adapted to snugly receive the end of the assembled sheath structure. A nut 204 surrounds the sheath inwardly of the nozzle 200 and it is provided with a threaded part 205 adapted to engage the threaded portion 202 for securing the parts together. The nut 204 is further provided with an outer un-threaded portion 206 that tapers outwardly to a diameter less than that of the flexible finger portion 203. Therefore, as the end 204 is screwed upon the part 202, the fingers 203 are forced inwardly to grippingly engage and lock the end attachment unit to the sheath. The ends of the fingers 203 are turned inwardly slightly as at 202 so that they grip the sheath in such a manner as to prevent endwise slipping of the attachment unit therefrom. With the parts thus assembled, the opposite ends of the spring wire I93 abut the respective shanks 200 and this is also true of the outer sheath structure around the wire I93; so that, when the end attachment fitting is secured in place as described, the parts of the sheath are not permitted to move endwise relatively to each other thereby insuring the non-contractible and non-expansible features above mentioned.

General operation In the operation of the structure so far described, the piece of work to be shaped is first secured in the vise 42 on the work table. The work table is then adjusted to the proper vertical position for shaping this particular piece of work. The tool head 39 is then adjusted in the ram 38 so as to position the tool 40 in proper relation with respect to the work or the portion of the work where the shaping cut is to be made. After that has been done, the position of the stroke of the ram is properly set, if that need be done; and, upon determining the length of the stroke or the length of the cut, the crank 65 is adjusted to give that particular stroke. To aid in making this adjustment, the rocker 10 is provided with a scale 2I0, along one side adjacent the slideway 80, and the crank block 8i which slides therein is provided with an indicating mark 2 adapted to register with the graduations on the scale 2I0. The graduations of the scale 2I0 may take any suitable form each representing a certain stroke length. To set the stroke, the gear 60 is rotated to a position wherein the crank 65 and rocker 10 are substantially parallel with the crank alignedwith the slideway 80. The nut 08 on the end of the stud 68 is then loosened, freeing the crank 65 for slide movement, and the crank, along with the block 8I, is moved up or down until the mark 2 on the block coincides with the proper graduation on the rocker scale 2I0 corresponding to the length of stroke desired. The nut t8 is again tightened, clamping the crank 65 in adjusted position as hereinabove explained.

In originally setting the machine, it may be necessary to regulate the extent of lateral feed of the work table to suit the particular shaping operation to be carried out. To this end, I provide structure which enables the lateral feed stroke to be lengthened or shortened. More particularly, referring to Figs. 12 to 15, inclusive, the bearing bracket I55 adjacent the gear I53 is of reduced diameter to receive the hub 2200f a cylindrical plate memer 22I extending along the side of the gear I53 and having laterally extending separated peripheral flanges 222 and 223 which overlie, in spaced relation, the teeth of the gear I53. The end 222 of the flange 222' and the end 223 of the flange 223 are spaced apart the same distance at all times and the pawl and ratchet structure for feeding the shaft I40 is ar-' ranged so that the pawl element picks up the teeth of the gear I53 between these spaced ends of these flanges. By rotating the disk22l to position the flanges 222 and 223 at different positions around the periphery of the gear I53 relative to the operating limits of the pawl structure, the pawl structure may be caused to pick up the gear I53 sooner or later in the operating stroke of the feed mechanism. That is to say, the pawl structure reciprocates between definite limits. By adjusting the flanges 222 and 223 counterclockwise around the gear I53, the pawl element ISI in its backward movement (Fig. 13) will override the plate flange 223 as shown in Fig. 14 so that, in its forward movementJ-t will not immediately pick up the gear I53, this being done only after the pawl member passes beyond the end of the flange element 223. By rotating the flanges 222 and 223 in the opposite direction, the pawl will pick up the gear sooner and will cause a greater feed stroke than in the previously described operation. This same adjustment and operation takes place in the reverse position of the pawl as shown in Fig. 15, the same as described above.

With the machine set in the above manner, the motor 35- is cut in thereby driving the gear 60 and, in turn, moving the rocker 10 back and forth under the control of the crank 55. This movement of the rocker causes forward and backward movement of the ram 38, during forward movement of which the shaping tool makes its out, and on the backward stroke the shaping tool is deflected out of operating relation to the work. The work table 4| remains stationary on the forward cutting stroke of the ram with the pawl mechanism set in the positions shown in Figs. 12 to 14, inclusive, the mechanism, including the eccentric structure above described, being so set that at this time the pawl structure is moving backwardly, and reaches the end of its backward stroke at the time the ram completes its forward stroke. As the latter starts its backward stroke, the pawl structure starts its forward stroke, moving the table laterally during the non-cutting operation of the cam. This operating sequence may be changed by changing the relative positions of the eccentric strap I82 and I83 relative to the operating positions of the crank That is to say, assuming that the relation of theparts shown in Fig. 10 is that which exists at the end of the back stroke of the ram, this condition may be reversed so that it exists atthe forward stroke of the ram by setting the eccentric I83 around 180 from the position shown in Fig. 10.

Modified work table drive connections The mechanism for transmitting intermittent lateral feed motion to the work table 4I may take various forms, some of which are illustrated in Figs. 18 to 24, inclusive. Referring to the form shown in Figs. 18 and 19, it includes a main drive gear 230'correspo-nding to the drive gear 60 offthe first form. The drive gear 230 supports a crank 23I similar to the crank 65 and is also arranged to directly impart reciprocatory movement to a feed wire 232 corresponding to the wire I15. Specifically, the outward face of the gear is pro-- vided with an inset plate member 233 having an annular, but eccentric, track 234. The side wall housing 235 adjacent the gear 2% is provided with a slot 236 through which projects an arm 231 connected tothe upper end of a piston-like slide block 238 to which the wire 232 is connected. The arm 231 is provided with a bifurcate end portion 239 which embraces the trackway 234 so that, as the gear 230 rotates, the eccentric track element 234 moves the bifurcations 233 of the arm to cause the piston 238 to reciprocate and transmit similar motion to the wire 232. Other than just described, the construction and operation of the feed mechanism may be the same as that of the first-described form.

The feed mechanism shown in Fig. 20 is similar to that of Figs. 18 and 19 except that the hub 248 of the main drive gear 24I (corresponding to the gears-60 and 230) is provided with a circumferentialslot 242, the base of which is shaped to provide an eccentric camway 243. The side wall of the housing 244 beneath the hub 246 supports a bracket 245 having a vertical chamber in which a piston-like block 246 is adapted to reciprocate. This block is connected to a feed wire 241 similar to the wires I15 and 232. The upper end of the piston block 246 is provided with a stem 248 proj ecting upwardly through an openin in the housing boss 249 with its inner end engaged in the slot 242 in seated relation against the camway 243. The piston block is constantly urged upwardly to hold the stem 248 in operating relation with "the camway 243 by a spring 259. This spring, in this manner, aids in reciprocating the piston 246 and, in turn, the feed wire 2&1. In this form, as the gear MI and its hub 240 rotate, the piston block 246 is caused to reciprocate, in turn reciprocating the wire 241 and causing lateral feed of the work support table.

The structure shown in Fig. 21 is similar to that of Fig. 20 except that the gear hub 265 is provided with a concentric cam slide 26! so constructed as to transmit motion in a direction axial of the hub 260. The feed wire 262 (similar to the feed wire 115) is connected to a piston block 253 r mounted to reciprocate in horizontal direction in a chamber in the housing carriage bracket 254. The piston block 263 is provided with a right angled upstanding arm 265, the end of which projects through the housing block 266 into the camslot 26I so that, as the main drive gear 261 (corresponding to gears till, 230 and MI) rotates, the piston block 263 and feed wire 262 are re ciprocated horizontally to transmit lateral feed motion to the work table.

In the feed mechanism shown in Fig. 22, the main drive gear 210 is provided on its outward face with an annular slot 21I of uniformly varying depth around its circumference providing a cam surface 212 adapted to transmit motion axially of the gear 216 as the latter is rotated. The sidewall of the housing 213 supports a bracket 214 having a chamber in which a piston slide block 215 is horizontally mounted. A feed wire 216 (similar to the feed Wires I15, 232, etc.)

is connected to the piston block 215 for reciprocation therewith. Reciprocation of the piston block 2151s accomplished by a stem 211 thereon whichaprojects through the side wall of the housing 213 into the cam slot 2' where it engages the cam surface 212. As the gear 210 rotates, the piston block 215 and wire 216 are reciprocated, in an obvious manner, to cause feed of the work table through mechanism which may be of a character similar to that already described. The piston block 215 is held in operative relation against the cam surface 212 by a spring 218 which functions similarly to the spring 250 of the form of Fig. 20.

In Figs, 23 and 24, I have shown a hydraulic means for transmitting feed motion from the main drive mechanism to the feed screw for moving the work table transversely. In this form, I employ a casing member 288 adapted to be carried by the machine housing in close proximity to the main driving mechanism, similarly to the bracket I18 of the first-described form. This casing is provided with a fluid chamber 28| in which is mounted a hydraulic piston member 282. This piston member may be pivotally connected at 283 to the main driving mechanism in any of the ways previously described. A flexible conduit 29!! is connected at one end to the fluid chamber 28! and at its other end to another similar fluid chamber contained in a casing member 284 (Fig. 24) corresponding to the casing or bracket portion I14 (Fig. 11) of the first form. The chamber of the casing member 284, corresponding to the fluid chamber 28I, is provided with a hydraulic piston (not shown) which is similar to the piston 28I and which is, in turn, connected by a link structure 285 to an arm 286 corresponding to the arm l 10 of the first form. The arm 288 is connected to a rock shaft 281 which is connected similarly to the rock shaft I54 (Fig. 11) to the feed mechanism directly connected with the work table for feeding ittransversely of the tool operating ram. The fluid chamber 28!, the conduit 290 and the chamber in the casing 284 are completely filled with a hydraulic fluid and, as the main drive mechanism moves the piston 282 downwardly, the piston in the casing 284 is moved upwardly raising the arm 286 and moving the rock shaft 281 in counterclockwise direction to apply a feed movement similarly to that described in connection with the first form. As the main drive mechanism operates to raise the piston 282, a spring 288, surrounding the rock shaft 281 and engaged at its opposite ends with a bearing 289 supporting the rock shaft and the arm 286, causes the arm 288 to move downwardly forcing the piston in the casing 284 and, in turn, forcing the fluid backwardly to condition the operating parts and the fluid in the manner illustrated in Figs. 23 and 24. Other than just described, the operation of this form is the same as that of the first-described form.

Summary of advantages It is believed that the advantages of my invention as hereinabove first stated will be well appreciated from the foregoing description. My invention supplies a need in the small workshop field. It provides a machine capable of performing a large number of shaping operations and which is so simple so far as operation and adjustment are concerned that it well serves the purpose in the hands of the unskilled as well as the skilled workman. It fills a distinct need in the manual training school field and other places where the use of the prior cumbersome, expensive and complicated shaping machines is prohibitive. My invention further provides a machine which, although of small size and inexpensive construction, is adapted to perform its work in a highly accurate manner and in much less time due to simplification of manipulation.

Although I have shown and described various forms of my invention, other changes in details and arrangement of parts may be made therein without departing from the spirit and scope of my invention as defined by the claims which follow.

I claim:

1. In structure of the class described, a work support, drive mechanism, and mechanism for feeding said work support in one direction which includes a feed member associated with said work support, a flexible member between said drive mechanism and said feed member reciprocable by said drive mechanism for imparting feed movement to said feed member, and means for guiding said flexible member in its reciprocating movement.

2. In structure of the class described, a work support, means for adjusting said work support in one direction, drive mechanism, and mechanism for feeding said work support in another direction which includes a feed member associated with said work support, a flexible member between said drive mechanism and said feed member reciprocable by said drive mechanism for imparting feed movement to said feed member in all adjusted positions of said work support without change in the operating relation between said drive mechanism and feed member, and means for guiding said flexible member in its reciprocating movement. I

3. In structure of the class described, a work support, drive mechanism, means for adjusting said work support in one direction, means including a feed member for moving said table in another direction, and means connecting said drive mechanism to said feed member for imparting feed movement to the latter, said connecting means including a reciprocable flexible member and means for guiding said flexible member whereby to accommodate said adjustment of said work table without breaking any connecting parts and without change in drive relation therebetween. i

4. In structure of the class described, a work support, drive mechanism, means for adjustably positioning said work support relative to a shaping tool, and means connecting said drive mechanism to said feed member for imparting feed movement to the latter, said means including a member reciprocably driven. by said drive mechanism, a second reciprocable member associated with said feed member for imparting movement to the latter, a flexible connection between said reciprocable members and through which reciprocation of the first of said reciprocable members is imparted to the second of said reciprocable members.

5. In structure of the class described, a work support, drive mechanism, means for adjusting said work support toward and from a shaping tool, a feed member connected to said-work support for feeding it transversely of its direction of adjustment, and means connecting said drive mechanism to said feed member for. imparting feed movement to the latter, said means including a member reciprocably driven by said drive mechanism, a second reciprocable member associated with said feed member for imparting movement to the latter, a flexible member between said reciprocable members and through which reciprocation of the first of said reciprocable members is imparted to the second of said reciprocable members, said flexible member being constructed to permit of bends and turns therein to accommodate said adjustment of said work support, and means sheathing said flexible member and constructed and arranged to prevent buckling of said flexible member when it is reciprocated.

6. In structure of the class described, a drive member, a work supporting table mounted for movements transversely of each other, means for moving said table in one direction, and means for moving said table transversely of said one direction in any position to which it may be adjusted in said one direction which includes a feed member operably connected to said table and which upon being actuated imparts lateral feed movement to said table, and means for imparting intermittent movement to said feed member including an elongated flexible drive connector adapted to be reciprocated, means for guiding said flexible connector in its reciprocating movement, a connection between one end of said connector and said drive member by which the former is reciprocated, and a connection between the other end of said drive connector and said feed member by which reciprocation of the former is transmitted to the latter.

7. In structure of the class described, a drive member, a work supporting table mounted for vertical and lateral movements, means for moving said table vertically, and means for moving said table laterally in all of its vertical positions which includes a feed member operably connected to said table and which upon being rotated imparts lateral feed movement to said table, and means for imparting intermittent rotative movement to said feed member including an elongated flexible drive connector adapted to be reciprocated, guide means for said flexible drive connector, a connection between one end of said connector and said drive member by which the former is reciprocated, gear means operably engaged with said feed member, and a pawl mechanism engageable with said gear means and con-' nected to the other end of said connector by which reciprocal movement of said connector is transmitted to said gearing for intermittent rotation of said feed member.

8. In structure of the class described, a drive member, a work supporting table mounted for movement back and forth and transversely thereof, means for moving said table back and forth, and means for moving said table transversely in all of its positions of back and forth movement which includes a feed member operably connected to said table and which upon being rotated imparts lateral feed movement to said table, meansfor imparting intermittent rotative movement to said feed member including an elongated flexible drive connector adapted to be reciprocated, guide means for said flexible connector, a connection between one end of said connector and said drive member by which the former is reciprocated, gear means associated with said feed member, a pawl mechanism connected to theother end of said connector comprising a pawl member adapted to engage said gear means positively upon movement in one direction to cause intermittent rotation of said feed member and adapted to ride freely over said gear means upon movement in the other direction, and means for reversing said pawl member whereby it is caused to ride freely over said gear means tool, which includes a feed member operably connected to said table and which upon being rotated imparts lateral feed movement to said table, means for imparting intermittent rotative movement to said feed member including an elongated fiexible drive connector adapted to be reciprocated, guide means for said flexible connector, a connection between one end of said connector and said drive member by which the former is reciprocated, gear means associated with said feed member, a pawl mechanism connected to the other end of said connector comprising a pawl member adapted to engage said gear means positively upon movement in one direction to cause intermittent rotation of said feed member and adapted to ride freely over said gear meansupon movement in the other direction, and means for varying the position of beginning of operative positive engagement between said gear means and said pawl member whereby the extent of each intermittent movement of said feed member may be varied.

10. In structure of the class described, a drive member, a work sup-porting table mounted for movement toward and from and transversely of a shaping tool, means for moving said table toward and from the shaping tool, and means for moving said table transversely in all of its positions of movement toward and from the shaping tool, which includes a feed member operably connected to said table and which upon being rotated imparts lateral feed movement to said table, and means for imparting intermittent movement to said feed member including an eccentric device operably connected to said drive member, a reciprocable element pivotally connected to said eccentric device, an elongated flexible drive connector rigidly connected to said reciprocable element, guide'mean's for said flexible connector, another reciprocable element rigidly connected to the other end of the drive connector, a pawl. mechanism operably connected to said other reciprocable element, and gear means operably connected to said feed member for the transmission of rotative movement thereto and adapted to be. engaged by said pawl mechanism for rotative movement of said feed member upon reciprocation of said reciprocable elements and drive connector by said eccentric device.

11. In structure of the class described, a drive member, a work supporting table mounted for movement toward and from and transversely of a shaping tool, means for moving said table toward and from the shaping tool, and means for moving said table transversely in all of its positions of movement toward and from the shaping tool, which includes a feed member operably connected to said table and which upon being rotated imparts lateral feed movement to said table, means for imparting intermittent movement to said feed member including an elonated flexible drive connector adapted to be re- 

